US5097899A

US5097899A - Shell with integral internal passage and method of making same

Info

Publication number: US5097899A
Application number: US07/357,883
Authority: US
Inventors: Jacob H. Martin; Charles S. Elder
Original assignee: Charles Stark Draper Laboratory Inc
Current assignee: Charles Stark Draper Laboratory Inc
Priority date: 1989-05-30
Filing date: 1989-05-30
Publication date: 1992-03-24
Anticipated expiration: 2009-05-30

Abstract

A formed non-planar heat exchanger having two non-planar plates continuously joined across their contacting surfaces and complementarily curved to form an integral curved member; at least one channel is formed in at least one of the plates to define an integral internal heat exchange fluid flow passage within the curve contour of the curved member; the integral internal heat exchange fluid flow passage conforms with the curved member. A method of making such a device is also disclosed.

Description

GOVERNMENT SPONSORSHIP

The invention disclosed herein was least partially developed with funds under U.S. Air Force Contract Nos. FO4704-86-C-0032; FO4704-87-C-0008; FO4704-88-C-0008; FO4704-86-C-0100.

FIELD OF INVENTION

This invention relates to a method and apparatus relating to a shell formed with one or more internal passageways, and more particularly to such a device adapted for use in a heat exchanger.

BACKGROUND OF INVENTION

Inertial guidance systems of all types, e.g. gimballed, laser, floating stable member, require a heat exchange system for removing heat from the internal volume of the housing in a controlled manner. Presently many heat exchange systems use separate tubes or channels which are brazed, soldered, glued or otherwise attached to the housing. Those tubes or channels conduct the coolant which carries the heat away from the internal inertial guidance system. The attachment of separate tubes is extremely labor intensive and expensive, and highly skilled personnel are required. In some cases the labor requirement and expense are further increased by the milling in the housing of grooves or gutters in which the tubes will nest, in order to improve surface-to-surface contact for heat conduction. Further, heat transfer into the separate tubes is not efficient or uniform. In addition, the separate externally mounted tubes are highly susceptible to damage during fabrication and throughout the life of the equipment. The need to solder the lengths of tubes to each other and to a manifold introduces the potential for leaks and the potential for blockages caused by excess solder creeping into the joints. Solder operations also leave flux residues that must be cleaned out. If the metals involved are not naturally solderable they must first be plated to enable soldering.

SUMMARY OF INVENTION

It is therefore an object of this invention to provide an improved method and apparatus for forming an internal passage in a curved member.

It is a further object of this invention to provide such an improved method and apparatus which is easier to make, requires less skilled personnel, less labor, and is less expensive to fabricate.

It is a further object of this invention to provide such an improved method and apparatus which has fewer parts relative to members having external passages.

It is a further object of this invention to provide such an improved apparatus which is adapted for use as a heat exchanger.

It is a further object of this invention to provide such an improved apparatus with better, more efficient heat transfer.

It is a further object of this invention to provide such an improved, more rugged heat exchanger in which there is less likelihood of damage to the heat exchange passages.

It is a further object of this invention to provide such an improved apparatus which eliminates the use of soldering techniques to install a passage and avoids the problem of solder blockages and flux residue in the passage.

This invention results from the realization that a more reliable, rugged, simpler, and more efficient heat exchanger could be achieved by making the normally external, separate heat exchanger fluid flow passages internal and integral, and the further realization that a heat exchanger shell or any shell could be fabricated with an integral internal passage by creating a groove in one or both of two plates, bonding the plates together to form a closed passage with the groove, and then converting or forming the plates into the desired shape such as a shell or dome or hemisphere by forming, drawing, bending, or the like.

This invention features a formed shell having an integral internal passage. The shell includes two non-planar plates which are continuously joined across their contacting surfaces and which are complementarily curved to form an integral curved shell. At least one channel is formed in at least one of the plates to define an integral internal fluid flow passage with the curved contours of the shell.

In preferred embodiments the passage may extend transverse to the forming direction or axis. The forming may include drawing, the plates may be brazed together, the shell may be domed or hemispherical. In one construction the shell forms a part of a heat exchanger which employs fluid flowing through the passage as the heat exchanging medium.

The invention also features a method of fabricating a shell having an integral internal passage. Two plates of malleable material are provided and a groove is created in at least one of those plates. The plates are then bonded together to create a closed internal passage from the groove. The bonded plates are then formed into a shell shape. The groove may be created extending generally transverse to the forming axis, the material may be aluminum, the bonding technique may be brazing, and the forming technique may include drawing, bending, or hydroforming.

In one technique the groove is filled before the forming step with a filler having a lower melting point than brazing material and the material of which the plates are made, and then after the forming step the shell is heated to extract the filler. When used as a heat exchanger, a manifold is mounted on the member or shell for accessing the internal integral passage.

DISCLOSURE OF PREFERRED EMBODIMENT

Other objects, features and advantages will occur to those skilled in the art from the following description of a preferred embodiment and the accompanying drawings, in which:

FIG. 1 is a simplified schematic sectional elevational view of a prior art inertial guidance device showing the heat exchanger equipment;

FIG. 2 is a top plan view of the prior art device of FIG. 1 showing the heat exchanger tubes;

FIG. 3 is a side elevational view of a completed prior art inertial measurement unit sphere also showing the external cooling tubes;

FIG. 4 is a schematic elevational sectional view of a shell with an internal integral passage made according to this invention for use in an inertial guidance device such as shown in FIGS. 1-3;

FIGS. 5A-D depict four steps in forming the shell of FIG. 4 according to this invention;

FIG. 6 is a top plan view of the shell of FIG. 4; and

FIG. 7 is a diagrammatic view of an axisymmetric shell made according to this invention having alternatively oriented passages in it.

There is shown in FIG. 1 a prior art inertial guidance device 10 which includes the stable member 12 hydraulically suspended inside power sphere 14. Power sphere 14 includes an upper, positive hemisphere 16 and a lower, negative hemisphere 18 which are joined together and electrically insulated from one another by equatorial ring 20. Surrounding power sphere 14 is heat transfer housing 22 which includes an upper section 24 and lower section 26.

Sections

24 and 26 each include

flanges

28 and 30, respectively, by which they are secured to equatorial ring 20. Fixed to the outside of

sections

24 and 26 is piping 32 and 34. These pipes are fastened to the outside of

sections

24 and 26 by gluing, soldering, brazing, or similar means. In some cases grooves are milled into the sections at added expense in order to improve the seating and heat transfer to

tubes

32 and 34. Manifold

caps

38 and 40 serve to introduce and exhaust cooling fluid to

tubes

32 and 34, and exhaust flotation fluid from the internal spherical annular volume 42 between power sphere 14 and

heat exchanger sections

24 and 26. Volume 42 functions as a variable resistance heat path. Flotation fluid such as FC-77 is driven from pump 50 through conduits 52 into

annular passages

54 and 56. From these passages which circle the device in

flanges

28 and 30, the FC-77 flows out into volume 42 toward

end caps

38 and 40, where it is exhausted at

ports

58 and 60 through

conduits

62 and 64 back to pump 50. A volume compensator 66 keeps the FC-77 at a relatively constant pressure, and a control circuit 68 drives the pump 50 to pump more or less fluid as a function of the temperature of the inertial guidance system as sensed by temperature sensor 70. The primary heat exchange system employs

tubes

32 and 34. Cooling fluid such as refrigerant R-12 is supplied by a source, not shown, through valve 80 and is recovered through valve 82. Incoming R-12 is provided through

conduits

84 and 86, provided with

expansion devices

88 and 90 to the inputs of

tubes

32 and 34, respectively, at

manifolds

38 and 40. The R-12 flows through the tubes toward the equatorial ring and then back up again to the

manifold caps

38 and 40, where the R-12 is exhausted through

conduits

92 and 94 to heat exchanger pressure control valve 82.

The complexity of the prior art heat

exchanger using tubes

32 and 34 can be seen more readily in FIG. 2, which shows a more detailed view of inertial guidance device 10 looking down from the top on the upper hemisphere 22. An even more vivid portrayal of the complexity of the prior art is shown in FIG. 3, which is a side elevational view of the inertial guidance device 10 with a mounting ring obscuring the equatorial ring.

In accordance with this invention, the heat exchanger housing is formed with an integral internal fluid flow passage for receiving the heat exchanging fluid such as shown in FIG. 4, where housing section 22a has been formed with two

curved members

100, 102, that form internal integral passage 104 in housing section 22a. The passage 104 is shown in curved plate 102 but may as well be in curved plate 100, or in both. The line 106 shows where the two

plates

100 and 102 were previously joined before being formed into the curved housing section 22a.

The heat exchanger section 22a is made according to the method of this invention as shown in FIGS. 5A-D. First a groove or a plurality of grooves 110, FIG. 5A, are formed in plate 112, which is then bonded such as by brazing to a second plate 114. The plates may be joined continuously over their contacting surface or discretely but sufficiently to produce sealed passages derived from the grooves. The plates or blank are made of a malleable material such as annealed aluminum. Typically plate 114 is thinner than plate 112, and so it is placed away from the hydraulic cylinder 116 to prevent it from being collapsed into grooves 110 during the forming process. The plates are then positioned on table 118, which contains a hole 120 for receiving steel punch 122. Hydraulic cylinder 116 is filled with hydraulic fluid 124 under pressure from a source not shown, and the bottom of cylinder 116 is sealed by a rubber diaphragm 126. At this time, or previously, the grooves may be filled with a material which has a lower melting temperature than

plates

112 and 114 and the brazing or joining material. These techniques prevent distortion of the grooves during the forming process. After the process is complete, the shell may be heated to flow the filler material, which may be for example Cerrobend.

Next, hydraulic cylinder 116 is lowered to contact the top of plate 112 and pressure is applied, FIG. 5B. Following this, as shown in FIG. 5C, steel punch 122 is driven upwardly along the longitudinal draw axis 111 and

plates

112 and 114 are formed about steel punch 122 against the pressure on diaphragm 126. The pressure of hydraulic fluid 124 is maintained, but fluid is allowed to escape as punch 122 rises. Finally, in FIG. 5D, the pressure of hydraulic cylinder 116 is released and the cylinder is raised. The blank is removed and the formed

plates

114 and 112 then have the lower portion 130 trimmed off to produce the final piece such as 22a, FIG. 4. Manifold cap 38a is then fastened to plate 114.

In one construction plate 112 is five-eighths inch thick and seventeen inches in diameter, provided with channels 0.156 inch wide and 0.110 inch deep; plate 114 is approximately one-eighth inch thick. Such a plate may begin as a square and end as shown in FIG. 6, with two sets of

grooves

140 and 142, each including a pair of

grooves

144, 146 and 148, 150, which extend parallel to each other, respectively, in a spiral directed inwardly toward the center. Grooves 144 and 146 are joined at junction 152 and

grooves

148 and 150 are connected at junction 154. Thus fluid introduced from a manifold cap through hole 156, spirals down through groove 148, across junction 154 to groove 150, and then up through hole 158 to the manifold cap. Likewise, fluid introduced through hole 156 to groove 144 enters groove 146 through junction 152 and exits through hole 158. The center hole 160 provides access to the internal heat exchange volume 42 as originally discussed in FIG. 1.

In the fabrication described in FIGS. 4 and 5A-5D, it is preferable to maintain the grooves generally transverse to the direction of forming for least groove deformation. Since the direction of forming is along the draw axis or longitudinal axis 111a, FIG. 6, then the groove should be maintained as much as possible parallel to the corresponding latitude lines.

Although thus far the shells formed have been shown as symmetrical about a forming axis, this is not a necessary limitation of the invention, for as shown in FIG. 7, the shell 170 can be asymmetrical. Similarly, although the grooves in FIGS. 4 through 6 are shown as generally transverse to the forming axis, this is also not a limitation of the invention, for as shown in FIG. 7 the grooves forming the passage 174 could meander generally in the direction of the longitudinal axis or forming axis 172 while locally meandering back and forth more parallel to the latitude lines symbolized at 176. Alternatively, passage 178 could meander generally in the direction of latitude line 176 while locally meandering generally parallel to the direction of the longitudinal axis or forming axis 172.

Although specific features of the invention are shown in some drawings and not others, this is for convenience only as each feature may be combined with any or all of the other features in accordance with the invention.

Other embodiments will occur to those skilled in the art and are with the following claims:

Claims

What is claimed is:

1. A domed heat exchanger comprising:

a metal base plate and a coextensive metal cover plate joined across their contacting surfaces and complementarily curved to form an integral domed member of substantially uniform thickness having substantially smooth inner and outer surfaces; and

at least one channel formed in at least one of said plates to define an integral internal heat exchange fluid flow passage within the curved contour of the domed member.

2. The domed heat exchanger of claim 1 in which said domed member is a hemisphere.

3. The domed heat exchanger of claim 1 in which said plates are brazed together.

4. The domed heat exchanger of claim 1 in which said base plate includes said at least one channel.

5. The domed heat exchanger of claim 1 further including a manifold on said member for accessing said passage.

6. A domed shell having an integral, internal fluid flow passage comprising:

two coextensive non-planar metal plates joined across their contacting surfaces and complementarily curved to form an integral domed shell of substantially uniform thickness having substantially smooth inner and outer surfaces; and

at least one channel formed in at least one of said plates to define the integral internal fluid flow passage within the curved contour of the domed shell.

7. The formed non-planar shell of claim 6 in which said plates are brazed together.

8. The formed non-planar shell of claim 6 in which said shell is hemispherical.

9. The formed non-planar shell of claim 6 in which said member is symmetrical about an axis.

10. The formed non-planar shell of claim 6 further including a manifold mounted on said shell for accessing said passage.

11. A hemispherical heat exchanger comprising:

two coextensive non-planar metal plates joined across their contacting surfaces and complementarily curved to form an integral hemispherical member of substantially uniform thickness having substantially smooth inner and outer surfaces; and

at least one channel formed in at least one of said plates to define an integral internal heat exchanger fluid flow passage within the curved contour of the hemispherical member.

12. The formed non-planar heat exchanger of claim 11 further including a manifold on said member for accessing said passage.

13. The formed non-planar heat exchanger of claim 11 in which said plates are brazed together.

14. The formed non-planar heat exchanger of claim 11 in which said member is symmetrical about an axis.

15. The formed non-planar heat exchanger of claim 11 in which said plates are joined continuously across their contacting surfaces.